US4714259A - Sealing ring structure with stressing ring - Google Patents

Sealing ring structure with stressing ring Download PDF

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Publication number
US4714259A
US4714259A US07/038,956 US3895687A US4714259A US 4714259 A US4714259 A US 4714259A US 3895687 A US3895687 A US 3895687A US 4714259 A US4714259 A US 4714259A
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US
United States
Prior art keywords
sealing ring
ring
stressing
sealing
recess
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/038,956
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English (en)
Inventor
Theo Mack
Roy Edlund
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Busak and Luyken GmbH and Co
Original Assignee
Busak and Luyken GmbH and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Busak and Luyken GmbH and Co filed Critical Busak and Luyken GmbH and Co
Assigned to BUSAK + LUYKEN GMBH & CO., HANDWERKERSTRASSE 5-7 7000 STUTTGART 1/GERMANY reassignment BUSAK + LUYKEN GMBH & CO., HANDWERKERSTRASSE 5-7 7000 STUTTGART 1/GERMANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: EDLUND, ROY, MACK, THEO
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Publication of US4714259A publication Critical patent/US4714259A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings

Definitions

  • the present invention relates to a sealing ring structure
  • a sealing ring structure comprising a sealing ring made of a tough-elastic plastic material fitted into the groove of one of two machine elements moving relative to each other, and a stressing ring made of a rubber-elastic material arranged between the said sealing ring and the bottom of the groove and loading the sealing ring in the radial direction, the axial extension of the said stressing ring being considerably smaller than that of the sealing ring and its axial position, relative to the sealing ring, being fixed by means of stops in such a manner that the sealing ring is loaded in the area of an edge.
  • German Disclosure Document No. 20 57 027 describes, for example, a hydraulic seal comprising a cylindrical sealing ring and a rubberelastic stressing ring which has its center arranged above one end of the cylindrical sealing ring so that it loads that end unilaterally.
  • the section of the stressing ring projecting beyond the sealing ring is supported by a, preferably, rigid supporting ring which does not perform any sealing functions. If this seal is to give perfect performance, it is necessary that very close tolerances be adhered to as regards the diameters of the sealing and the supporting rings relative to each other and also in relation to the diameter of the sealing surface, i.e. the diameter of the rod or shaft to be sealed.
  • the stressing ring of the sealing structure according to the invention acts upon an area of the sealing ring located between those areas of the sealing ring which rest against the sealing surface.
  • the sealing ring therefore, is permitted to deflect more or less without thereby affecting considerably the contact pressure exerted upon the sealing surface by the edges of the sealing ring which define the portions of the sealing ring on either side of the recess.
  • the sealing structure according to the invention ensures substantially constant contact pressure which is maintained even when dimensional changes occur due to temperature variations during operation of the sealing structure.
  • the contact pressures achievable by the seal according to the invention depend of course on the flexural stiffness of the tough-elastic plastic material of the sealing ring. Consequently, this seal can be used with advantage only for moderate pressures of up to approximately 150 bar. However, up to this moderate pressure range, the seal according to the invention provides a low-friction seal for pneumatic and hydraulic applications which is insensitive to tolerance and temperature changes and which distinguishes itself by perfect sealing performance and long service life.
  • the surface portions adjacent the annular recess are of conical shape so that in the relaxed condition the sealing ring is in contact with the other machine component by the edges adjacent its outer end faces.
  • the pressure and, thus, the deflection of the sealing ring rises, an increasing portion of the conical surfaces comes into contact with the other machine portion, while at the same time the pressure at the outer edges increases.
  • Both the rising pressure at the outer edges and the rising surface pressure in the area extending right to the inner recess lead to an improvement of the sealing effect as the pressure rises.
  • the sealing ring may be provided on its ends with webs projecting beyond the surface loaded by the stressing ring and resting against the bottom of the groove so as to prevent the sealing ring from giving way and to form abutments which contribute towards increasing the contact pressures. This increases the pressure loading capacity of the sealing structure according to the invention still further.
  • the stressing ring may be fixed relative to the sealing ring in different manners. It would be possible, for example, to fit supporting rings in the groove receiving the sealing ring and the stressing ring, on both sides of the latter. However, it is also imaginable to provide the side of the sealing ring facing the stressing ring with another recess serving to receive the stressing ring. However, this may lead to the stressing ring exerting upon the sealing ring axial forces that could influence its function in a disadvantageous manner.
  • a preferred embodiment of the invention therefore, provides that the groove receiving the sealing ring and the stressing ring is provided at its center with a recess which is engaged by the stressing ring. This ensures that the position of the stressing ring is determined perfectly and that only radially acting stressing forces, as required for the perfect operation of the sealing structure, are transmitted to the sealing ring.
  • FIG. 1 shows a cross-section through the sealing ring of a sealing structure according to the invention, in relaxed condition
  • FIG. 2 shows a sealing structure according to the invention using the sealing ring illustrated in FIG. 1.
  • FIG. 1 shows the cross-section of a sealing ring in relaxed condition.
  • the sealing ring 1 consists of a tough-elastic plastic material, for example a material on a PTFE or polyurethane basis. Its cylindrical main body is provided on one side with a central recess 2.
  • the legs 3 defining the recess 2 exhibit inclined end faces 4 defining with a concentrical cylindrical surface 5, which is in contact with the ends of the legs 3, an angle ⁇ opening towards the recess 2.
  • the other side of the sealing ring carries on its ends two webs 6.
  • the sealing ring 1 is mounted, together with a rubber-elastic stressing ring 11, in the groove 12 of one of two components 13, 14 to be sealed relative to each other so that the end faces 4 on the ends of its webs 3 are in contact with the sealing surface 15 of the other component 14.
  • the groove 12 is sized in such a manner that the sealing ring 1 is received in the groove with little axial play and has its webs 6 in contact with the bottom of the groove 12.
  • the rubber-elastic stressing ring 11 engages a recess 16 provided in the central area of the groove 12.
  • the rubber-elastic stressing ring 11 is a simple O ring.
  • the diameter of the stressing ring 11 is smaller than the axial length of the recess 2 in the sealing ring 1 so that the stressing ring 1 does not act upon a rigid abutment, but rather on an unsupported area of the sealing ring. Consequently, the sealing ring 1 deflects as indicated in FIG. 2. The degree of deflection may be sufficient to bring the inclined faces 4 on the ends of the legs 3 into contact with the sealing surface 15 of the other component 14, a condition which is also indicated in FIG. 2.
  • the contact pressure between the end faces 4 of the legs 3 and the sealing surface 15 is determined substantially by the stressing force of the stressing ring 11, which is largely independent of minor differences in diameter. Accordingly, this contact pressure is independent of tolerances in the diameter of the other machine component 14 and also of the inner diameter of the recess 16 and the outer diameter of the sealing ring.
  • the sealing ring given the fact that the portions of the sealing ring which are in contact with the machine component 14 are resilient in radial direction, the sealing ring itself is also capable of adapting itself easily to different diameters of the other machine component 14.
  • the sealing arrangement according to the invention is relatively insensitive to production tolerances. And its operation also is not impaired by dimensional changes due to temperature variations which makes the seal according to the invention excellently suited, in particular, for applications where important temperature variations are encountered.
  • the deformation of the sealing ring 1 commences by a tilting movement about the edges 7 of the sealing ring until the end faces 4 rest flat against the sealing surface 15, as shown in FIG. 2. Any further deflection of the central portion 1 would create a tendency for the sealing ring to tilt about its inner edges 8, and this in turn would cause the sealing ring to get out of contact with the sealing surface 15 in the area of its outer edges 7--an effect which is rather undesirable. This effect is avoided in the embodiment shown by the webs 6 provided on the ends of the sealing ring and resting against the bottom of the groove 12 thereby preventing any undesirable deformation of the sealing ring.
  • the sealing ring may be a cylindrical body provided only with a central recess, but having no outer webs on its ends and no inclined surfaces on the ends of the legs. It is, however, also imaginable to arrange the conical surfaces in such a manner that they include between them an outwardly opening angle so that in the relaxed condition the sealing ring rests against the sealing surface by the edges defining the annular recess.
  • the angle ⁇ included between the sealing surface and the surface of the seal may be in the range of approximately -15° to +15°.
  • the recess serving to receive the stressing ring may be formed also by a deeper groove in which two supporting rings are arranged on either side of the stressing ring.
  • a sealing structure according to the invention may be arranged either on the periphery of a piston or in a component serving for supporting and guiding a rod.
  • the seal according to the invention is also excellently suited for use as an oil seal.
  • it may also be used for sealing off fluids of any type. In particular, it is suited as seal for both pneumatic and hydraulic systems.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
US07/038,956 1986-04-24 1987-04-16 Sealing ring structure with stressing ring Expired - Fee Related US4714259A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3613880 1986-04-24
DE3613880A DE3613880C1 (de) 1986-04-24 1986-04-24 Dichtungsanordnung

Publications (1)

Publication Number Publication Date
US4714259A true US4714259A (en) 1987-12-22

Family

ID=6299442

Family Applications (1)

Application Number Title Priority Date Filing Date
US07/038,956 Expired - Fee Related US4714259A (en) 1986-04-24 1987-04-16 Sealing ring structure with stressing ring

Country Status (5)

Country Link
US (1) US4714259A (de)
EP (1) EP0242741B1 (de)
JP (1) JPS62261762A (de)
DE (1) DE3613880C1 (de)
DK (1) DK205687A (de)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4889351A (en) * 1988-05-12 1989-12-26 Frost Stanley A Hydraulic seal
US4953876A (en) * 1987-11-17 1990-09-04 Busak & Luyken Gmbh & Co. Sealing ring structure
US5050892A (en) * 1989-03-09 1991-09-24 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Sealing arrangement for piston in compressor
EP0455924A1 (de) * 1989-12-29 1991-11-13 W.S. Shamban Europa A/S Eingefangene Dichtung zwischen sich gegeneinander bewegenden Flächen
US5066027A (en) * 1987-12-23 1991-11-19 Busak + Luyken Gmbh & Co. Sealing ring apparatus
US5083593A (en) * 1989-09-21 1992-01-28 Fogg Filler Co. Flip-flop seal
US5156410A (en) * 1987-03-20 1992-10-20 W.S. Shamban Europa A/S (W.S. Shamban & Company A/S) Combination seal for sealing between two machine parts
US5395125A (en) * 1992-03-06 1995-03-07 Hydro Rene Leduc Rotating joint for hydraulic system
US5467689A (en) * 1991-08-28 1995-11-21 Eaton Corporation Hydraulic cylinder and biased wear ring assembly for use therein
US5474307A (en) * 1990-08-06 1995-12-12 Richard DeBiasse Piston ring employing elastomeric sealing member within the ring groove
US5674055A (en) * 1994-05-16 1997-10-07 Pgi International, Ltd. Piston sealing arrangement for a sampling pump system
US5755446A (en) * 1996-12-24 1998-05-26 United Technologies Corporation Seal apparatus between a shaft and a non-linear inner surface of a housing
US6135008A (en) * 1998-03-16 2000-10-24 Haldex Brake Corporation Piston with lubricant-scraping ring and lubricant return ports
US6502826B1 (en) * 2000-10-30 2003-01-07 Caterpillar Inc Hydraulic cylinder piston seal
US20040227300A1 (en) * 2002-03-14 2004-11-18 Iwan Wolf Device for sealing a gap
DE10356813A1 (de) * 2003-12-05 2005-07-07 Zf Transmission Technologies L.L.C., Batavia Gleitdichtung einer Kolben/Zylinder-Einheit
US7191875B2 (en) * 2001-08-01 2007-03-20 Honda Giken Kogyp Kabushiki Kaisha Disc brake
US20230160470A1 (en) * 2020-02-12 2023-05-25 Cross Manufacturing Company (1938) Limited Shaft mounting assembly

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3821873A1 (de) * 1988-06-29 1990-02-08 Busak & Luyken Gmbh & Co Dichtungsanordnung
DE3940324A1 (de) * 1989-12-06 1991-06-13 Freudenberg Carl Fa Kolben- oder stangendichtung
DE4017036C2 (de) * 1990-05-26 1994-01-27 Busak & Luyken Gmbh & Co Dichtungsanordnung
DE9315357U1 (de) * 1993-10-11 1995-02-16 Martin Merkel GmbH & Co KG, 21107 Hamburg Dichtungsanordnung

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US28105A (en) * 1860-05-01 Peters
US2784013A (en) * 1953-12-21 1957-03-05 Bendix Aviat Corp Hydraulic seal
US3033578A (en) * 1959-08-10 1962-05-08 Gen Motors Corp Fluid seal
US3268235A (en) * 1965-03-29 1966-08-23 Alphonse A Jacobellis Piston accumulator seal
DE2057027A1 (de) * 1970-11-20 1972-05-25 Fichtel & Sachs Ag Hydraulische Dichtung
USRE28105E (en) 1972-09-22 1974-08-06 Sealing assembly
US4179131A (en) * 1976-11-23 1979-12-18 Patent & Inventions Ltd. Seal arrangements
US4239242A (en) * 1978-12-18 1980-12-16 Burns William G Pipe union and seal
GB2096247A (en) * 1981-04-03 1982-10-13 Welding The Inst Sliding vacuum seal
DE8325499U1 (de) * 1984-01-26 A. Römheld GmbH & Co KG, 6312 Laubach Ringdichtung zum Abdichten von beweglichen Körpern

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2222416C3 (de) * 1972-05-06 1975-07-03 Nabenfabrik Alfing Kessler Kg, 7083 Wasseralfingen Dichtungsanordnung für den Kolben eines hydropneumatischen Speichers
US4566703A (en) * 1981-04-24 1986-01-28 Microdot Incorporated Seal assembly
FR2525313A1 (fr) * 1982-04-19 1983-10-21 Joint Francais Joint d'etancheite en elastomere
US4496161A (en) * 1982-10-25 1985-01-29 The Gates Rubber Company Radially extensible joint packing with O-ring

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US28105A (en) * 1860-05-01 Peters
DE8325499U1 (de) * 1984-01-26 A. Römheld GmbH & Co KG, 6312 Laubach Ringdichtung zum Abdichten von beweglichen Körpern
US2784013A (en) * 1953-12-21 1957-03-05 Bendix Aviat Corp Hydraulic seal
US3033578A (en) * 1959-08-10 1962-05-08 Gen Motors Corp Fluid seal
US3268235A (en) * 1965-03-29 1966-08-23 Alphonse A Jacobellis Piston accumulator seal
DE2057027A1 (de) * 1970-11-20 1972-05-25 Fichtel & Sachs Ag Hydraulische Dichtung
USRE28105E (en) 1972-09-22 1974-08-06 Sealing assembly
US4179131A (en) * 1976-11-23 1979-12-18 Patent & Inventions Ltd. Seal arrangements
US4239242A (en) * 1978-12-18 1980-12-16 Burns William G Pipe union and seal
GB2096247A (en) * 1981-04-03 1982-10-13 Welding The Inst Sliding vacuum seal

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5156410A (en) * 1987-03-20 1992-10-20 W.S. Shamban Europa A/S (W.S. Shamban & Company A/S) Combination seal for sealing between two machine parts
US4953876A (en) * 1987-11-17 1990-09-04 Busak & Luyken Gmbh & Co. Sealing ring structure
US5066027A (en) * 1987-12-23 1991-11-19 Busak + Luyken Gmbh & Co. Sealing ring apparatus
US4889351A (en) * 1988-05-12 1989-12-26 Frost Stanley A Hydraulic seal
US5050892A (en) * 1989-03-09 1991-09-24 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Sealing arrangement for piston in compressor
US5083593A (en) * 1989-09-21 1992-01-28 Fogg Filler Co. Flip-flop seal
EP0455924A1 (de) * 1989-12-29 1991-11-13 W.S. Shamban Europa A/S Eingefangene Dichtung zwischen sich gegeneinander bewegenden Flächen
US5474307A (en) * 1990-08-06 1995-12-12 Richard DeBiasse Piston ring employing elastomeric sealing member within the ring groove
US5467689A (en) * 1991-08-28 1995-11-21 Eaton Corporation Hydraulic cylinder and biased wear ring assembly for use therein
US5395125A (en) * 1992-03-06 1995-03-07 Hydro Rene Leduc Rotating joint for hydraulic system
US5674055A (en) * 1994-05-16 1997-10-07 Pgi International, Ltd. Piston sealing arrangement for a sampling pump system
US5755446A (en) * 1996-12-24 1998-05-26 United Technologies Corporation Seal apparatus between a shaft and a non-linear inner surface of a housing
US6135008A (en) * 1998-03-16 2000-10-24 Haldex Brake Corporation Piston with lubricant-scraping ring and lubricant return ports
US6502826B1 (en) * 2000-10-30 2003-01-07 Caterpillar Inc Hydraulic cylinder piston seal
US7191875B2 (en) * 2001-08-01 2007-03-20 Honda Giken Kogyp Kabushiki Kaisha Disc brake
US20040227300A1 (en) * 2002-03-14 2004-11-18 Iwan Wolf Device for sealing a gap
DE10356813A1 (de) * 2003-12-05 2005-07-07 Zf Transmission Technologies L.L.C., Batavia Gleitdichtung einer Kolben/Zylinder-Einheit
US20230160470A1 (en) * 2020-02-12 2023-05-25 Cross Manufacturing Company (1938) Limited Shaft mounting assembly
US12442403B2 (en) * 2020-02-12 2025-10-14 Cross Manufacturing Company (1938) Limited Shaft mounting assembly

Also Published As

Publication number Publication date
JPS62261762A (ja) 1987-11-13
EP0242741A3 (en) 1988-05-25
DK205687D0 (da) 1987-04-23
EP0242741A2 (de) 1987-10-28
DK205687A (da) 1987-10-25
DE3613880C1 (de) 1987-07-02
EP0242741B1 (de) 1990-07-25

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Owner name: BUSAK + LUYKEN GMBH & CO., HANDWERKERSTRASSE 5-7 7

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